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JP6580518B2 - Intake device for internal combustion engine - Google Patents

Intake device for internal combustion engine Download PDF

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Publication number
JP6580518B2
JP6580518B2 JP2016095899A JP2016095899A JP6580518B2 JP 6580518 B2 JP6580518 B2 JP 6580518B2 JP 2016095899 A JP2016095899 A JP 2016095899A JP 2016095899 A JP2016095899 A JP 2016095899A JP 6580518 B2 JP6580518 B2 JP 6580518B2
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egr gas
bank
pipe
sectional area
channel
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JP2017203421A (en
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満季 浅井
満季 浅井
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Toyota Industries Corp
Toyota Motor Corp
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Toyota Industries Corp
Toyota Motor Corp
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Priority to JP2016095899A priority Critical patent/JP6580518B2/en
Priority to EP17795886.5A priority patent/EP3456952B1/en
Priority to US16/098,903 priority patent/US10697402B2/en
Priority to PCT/JP2017/015239 priority patent/WO2017195525A1/en
Publication of JP2017203421A publication Critical patent/JP2017203421A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/19—Means for improving the mixing of air and recirculated exhaust gases, e.g. venturis or multiple openings to the intake system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/44—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which a main EGR passage is branched into multiple passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
    • F02M35/10222—Exhaust gas recirculation [EGR]; Positive crankcase ventilation [PCV]; Additional air admission, lubricant or fuel vapour admission
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10242—Devices or means connected to or integrated into air intakes; Air intakes combined with other engine or vehicle parts
    • F02M35/10262—Flow guides, obstructions, deflectors or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/104—Intake manifolds
    • F02M35/116—Intake manifolds for engines with cylinders in V-arrangement or arranged oppositely relative to the main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/20—Feeding recirculated exhaust gases directly into the combustion chambers or into the intake runners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/12—Devices or methods for making a gas mixture for a combustion engine
    • F02M2700/126—Devices for the supply or mixing of air and gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/43—Arrangements for supplying air, fuel or auxiliary fluids to a combustion space of mixture compressing engines working with liquid fuel
    • F02M2700/4302—Arrangements for supplying air, fuel or auxiliary fluids to a combustion space of mixture compressing engines working with liquid fuel whereby air and fuel are sucked into the mixture conduit
    • F02M2700/4373—Mixture improving devices
    • F02M2700/4376—Mechanical devices
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Description

本発明は、内燃機関の吸気装置に関するものである。   The present invention relates to an intake device for an internal combustion engine.

内燃機関のＥＧＲシステムにおいては排気ガスの一部をＥＧＲガスとして吸気系に還流するために吸気管にＥＧＲガス管を接続している。特許文献１においては多気筒エンジンの吸気通路分岐部にＥＧＲガス管を接続するとともに傘状の流れ変更手段を設けて吸入空気流とＥＧＲガス流とを対向衝突させないようにする技術が開示されている。   In an EGR system of an internal combustion engine, an EGR gas pipe is connected to an intake pipe in order to return a part of exhaust gas as EGR gas to the intake system. Patent Document 1 discloses a technique for connecting an EGR gas pipe to an intake passage branch of a multi-cylinder engine and providing an umbrella-shaped flow changing means so that the intake air flow and the EGR gas flow do not face each other. Yes.

特開平９−８８７４５号公報JP-A-9-88745

ところで、Ｖ型エンジン等の左右のバンクを有する内燃機関においてＥＧＲガスを吸気系に還流する場合には、気筒間におけるＥＧＲ率のばらつきを低減させるために左右のバンクに流すＥＧＲガスの量を均等化する必要がある。   By the way, when the EGR gas is recirculated to the intake system in an internal combustion engine having left and right banks such as a V-type engine, the amount of EGR gas flowing to the left and right banks is equalized in order to reduce the variation in the EGR rate between cylinders. It is necessary to make it.

本発明の目的は、第１バンク及び第２バンクに流すＥＧＲガスの量を均等化することができる内燃機関の吸気装置を提供することにある。   An object of the present invention is to provide an intake device for an internal combustion engine that can equalize the amount of EGR gas flowing through the first bank and the second bank.

請求項１に記載の発明では、新気が流れる１本の新気吸気管に分岐部を介して第１バンク用と第２バンク用の２本の分岐管が接続された吸気管と、前記吸気管にＥＧＲガスを導入するためのＥＧＲガス管と、を備える内燃機関の吸気装置であって、前記ＥＧＲガス管が前記吸気管の前記分岐部に接続され、前記吸気管内における前記ＥＧＲガス管の開口部の周囲に、ＥＧＲガスが流入するとともにＥＧＲガスが第１バンク及び第２バンクに向けて流出するＥＧＲガス溜め室を区画形成するための隔壁部材が配置され、前記ＥＧＲガス溜め室におけるＥＧＲガスが第１バンクに向けて流出する第１バンク用流路での有効断面積及び第２バンクに向けて流出する第２バンク用流路での有効断面積が前記ＥＧＲガス管の開口部での流路断面積より小さくされていることを要旨とする。   In the first aspect of the present invention, an intake pipe in which two branch pipes for the first bank and the second bank are connected to one fresh air intake pipe through which a fresh air flows through a branch portion; An intake system for an internal combustion engine comprising an EGR gas pipe for introducing EGR gas into the intake pipe, wherein the EGR gas pipe is connected to the branch portion of the intake pipe, and the EGR gas pipe in the intake pipe A partition member for defining an EGR gas reservoir chamber in which EGR gas flows in and flows out toward the first bank and the second bank is disposed around the opening of the EGR gas reservoir. The effective sectional area in the first bank flow path through which EGR gas flows out toward the first bank and the effective sectional area in the second bank flow path through which the EGR gas flows out toward the second bank are the openings of the EGR gas pipe. Smaller than the channel cross-sectional area at Rot can be summarized as is.

請求項１に記載の発明によれば、ＥＧＲガス管のＥＧＲガス流入口が吸気管の分岐部に接続され、吸気管内におけるＥＧＲガス管の開口部の周囲に配置された隔壁部材によりＥＧＲガス溜め室が区画形成され、ＥＧＲガスが流入するとともにＥＧＲガスが第１バンク及び第２バンクに向けて流出する。また、ＥＧＲガス溜め室におけるＥＧＲガスが第１バンクに向けて流出する第１バンク用流路での有効断面積及び第２バンクに向けて流出する第２バンク用流路での有効断面積がＥＧＲガス管の開口部での流路断面積より小さくされている。これにより、新気及びＥＧＲガスは第１バンクと第２バンクとで交互に吸気されるが、この脈動に対してＥＧＲガスで満たされた容積を確保することができ、第１バンク及び第２バンクに流すＥＧＲガスの量を均等化することができる。   According to the first aspect of the present invention, the EGR gas reservoir is connected to the EGR gas inlet of the EGR gas pipe connected to the branch portion of the intake pipe, and is arranged around the opening of the EGR gas pipe in the intake pipe. A chamber is defined, and EGR gas flows in and flows out toward the first bank and the second bank. In addition, the effective cross-sectional area in the first bank flow path where EGR gas in the EGR gas reservoir chamber flows out toward the first bank and the effective cross-sectional area in the second bank flow path out toward the second bank are It is made smaller than the channel cross-sectional area at the opening of the EGR gas pipe. As a result, fresh air and EGR gas are alternately sucked in the first bank and the second bank, but the volume filled with the EGR gas can be secured against this pulsation, and the first bank and the second bank. The amount of EGR gas flowing to the bank can be equalized.

請求項２に記載のように、請求項１に記載の内燃機関の吸気装置において、前記第１バンク用流路での実断面積及び前記第２バンク用流路での実断面積が前記ＥＧＲガス管の開口部での流路断面積より小さいことにより、前記第１バンク用流路での有効断面積及び第２バンク用流路での有効断面積が前記ＥＧＲガス管の開口部での流路断面積より小さくされているとよい。   According to a second aspect of the present invention, in the intake device for an internal combustion engine according to the first aspect, an actual sectional area of the first bank channel and an actual sectional area of the second bank channel are the EGR. By being smaller than the flow path cross-sectional area at the opening of the gas pipe, the effective cross-sectional area at the first bank flow path and the effective cross-sectional area at the second bank flow path are at the opening of the EGR gas pipe. It may be smaller than the cross-sectional area of the channel.

請求項３に記載のように、請求項１に記載の内燃機関の吸気装置において、前記第１バンク用流路での実断面積及び前記第２バンク用流路での実断面積が前記ＥＧＲガス管の開口部での流路断面積より大きく、かつ、前記ＥＧＲガス溜め室におけるＥＧＲガスの流路での絞りにより、前記第１バンク用流路での有効断面積及び第２バンク用流路での有効断面積が前記ＥＧＲガス管の開口部での流路断面積より小さくされているとよい。   According to a third aspect of the present invention, in the intake device for an internal combustion engine according to the first aspect, the actual cross-sectional area in the first bank flow path and the actual cross-sectional area in the second bank flow path are the EGR. The effective cross-sectional area in the first bank flow path and the second bank flow are larger than the flow path cross-sectional area in the opening of the gas pipe, and by the restriction in the EGR gas flow path in the EGR gas reservoir chamber. The effective cross-sectional area in the path is preferably smaller than the cross-sectional area of the flow path at the opening of the EGR gas pipe.

請求項４に記載のように、請求項１〜３のいずれか１項に記載の内燃機関の吸気装置において、前記隔壁部材は、新気吸気管の開口部に向かって凸となる形状を有するとよい。   According to a fourth aspect of the present invention, in the intake device for an internal combustion engine according to any one of the first to third aspects, the partition member has a shape that protrudes toward the opening of the fresh air intake pipe. Good.

本発明によれば、第１バンク及び第２バンクに流すＥＧＲガスの量を均等化することができる。   According to the present invention, the amount of EGR gas flowing through the first bank and the second bank can be equalized.

実施形態における内燃機関の吸気装置の概略平面図。1 is a schematic plan view of an intake device for an internal combustion engine in an embodiment. 内燃機関の吸気装置の一部斜視図。The partial perspective view of the intake device of an internal combustion engine. 内燃機関の吸気装置の一部斜視図。The partial perspective view of the intake device of an internal combustion engine. （ａ）は内燃機関の吸気装置の一部断面図、（ｂ）は（ａ）のＡ矢視図。(A) is a partial cross section figure of the intake device of an internal combustion engine, (b) is the A arrow directional view of (a). 別例の内燃機関の吸気装置の一部断面図。The partial cross section figure of the intake device of the internal combustion engine of another example. 別例の内燃機関の吸気装置の一部断面図。The partial cross section figure of the intake device of the internal combustion engine of another example. 別例の内燃機関の吸気装置の一部断面図。The partial cross section figure of the intake device of the internal combustion engine of another example. 別例の内燃機関の吸気装置の一部断面図。The partial cross section figure of the intake device of the internal combustion engine of another example. （ａ）は別例の内燃機関の吸気装置の一部断面図、（ｂ）は（ａ）のＢ矢視図。(A) is a partial cross-sectional view of an intake device of an internal combustion engine of another example, (b) is a view taken in the direction of arrow B in (a).

以下、本発明を具体化した一実施形態を図面に従って説明する。
なお、本実施形態では、発明の構造を理解しやすいように、各図面において、互いに直交するＸ軸、Ｙ軸、Ｚ軸により３次元空間の直交座標系を規定している。 DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings.
In the present embodiment, an orthogonal coordinate system in a three-dimensional space is defined by an X axis, a Y axis, and a Z axis that are orthogonal to each other so that the structure of the invention can be easily understood.

図１に示すように、本実施形態における内燃機関の吸気装置１０は、吸気管２０と、吸気管２０にＥＧＲガスを導入するためのＥＧＲガス管３０を備えている。吸気管２０は、１本の新気吸気管２１と、新気吸気管２１から分岐する２本の分岐管２２，２３とを有する。吸気管２０は、新気が流れる１本の新気吸気管２１に分岐部２４を介して右バンク用と左バンク用の２本の分岐管２２，２３が接続されている。   As shown in FIG. 1, the intake device 10 for an internal combustion engine in the present embodiment includes an intake pipe 20 and an EGR gas pipe 30 for introducing EGR gas into the intake pipe 20. The intake pipe 20 has one fresh air intake pipe 21 and two branch pipes 22 and 23 branched from the fresh air intake pipe 21. In the intake pipe 20, two branch pipes 22 and 23 for the right bank and the left bank are connected to one fresh air intake pipe 21 through which fresh air flows through a branch portion 24.

車両に内燃機関５０が搭載されており、内燃機関５０の出力が変速機を介して車輪に伝達される。この実施形態では、内燃機関５０として、Ｖ型の６気筒ディーゼルエンジンを用いた場合を示している。内燃機関５０は、第１バンクとしての右バンク５１と第２バンクとしての左バンク５２とを有しており、右バンク５１には３気筒が、左バンク５２には３気筒が配置されている。   An internal combustion engine 50 is mounted on the vehicle, and the output of the internal combustion engine 50 is transmitted to wheels via a transmission. In this embodiment, a case where a V-type 6-cylinder diesel engine is used as the internal combustion engine 50 is shown. The internal combustion engine 50 has a right bank 51 as a first bank and a left bank 52 as a second bank. Three cylinders are arranged in the right bank 51, and three cylinders are arranged in the left bank 52. .

内燃機関５０には、内燃機関５０より排出される排気ガスが流れる排気管５５が接続されている。排気管５５は、右バンク用排気管５５ａと左バンク用排気管５５ｂを有する。排気管５５には、排気ガスの一部を吸気系に戻すための、ＥＧＲガス管３０が接続されている。ＥＧＲガス管３０は、右バンク用ＥＧＲガス管３１ａと、左バンク用ＥＧＲガス管３１ｂと、右バンク用ＥＧＲガス管３１ａと左バンク用ＥＧＲガス管３１ｂとが集合した集合ＥＧＲガス管３１ｃを有する。   An exhaust pipe 55 through which exhaust gas discharged from the internal combustion engine 50 flows is connected to the internal combustion engine 50. The exhaust pipe 55 includes a right bank exhaust pipe 55a and a left bank exhaust pipe 55b. The exhaust pipe 55 is connected to an EGR gas pipe 30 for returning a part of the exhaust gas to the intake system. The EGR gas pipe 30 includes a right bank EGR gas pipe 31a, a left bank EGR gas pipe 31b, and an aggregate EGR gas pipe 31c in which the right bank EGR gas pipe 31a and the left bank EGR gas pipe 31b are assembled. .

図２，３に示すように、分岐管２２，２３は分岐部２４において新気吸気管２１から分岐している。分岐管２２は右バンク５１用であり、分岐管２３は左バンク５２用である。新気吸気管２１は円管であり、分岐管２２，２３は円管である。   As shown in FIGS. 2 and 3, the branch pipes 22 and 23 branch from the fresh air intake pipe 21 at the branch portion 24. The branch pipe 22 is for the right bank 51, and the branch pipe 23 is for the left bank 52. The fresh air intake pipe 21 is a circular pipe, and the branch pipes 22 and 23 are circular pipes.

新気吸気管２１は、分岐部２４においてＺ軸に沿って延びている。分岐管２２，２３は、それぞれ、分岐部２４において、Ｘ軸に沿って互いに離間する方向に延びている。
排気ガスが流れる排気管に一端が接続されたＥＧＲガス管３０を介して、内燃機関より排出された排気ガスの一部がＥＧＲガスとして吸気系に戻される。吸気管２０の分岐部２４にはＥＧＲガス管３０が連結されている。 The fresh air intake pipe 21 extends along the Z axis at the branch portion 24. Each of the branch pipes 22 and 23 extends in the branch portion 24 in a direction away from each other along the X axis.
A part of the exhaust gas discharged from the internal combustion engine is returned to the intake system as EGR gas via the EGR gas pipe 30 having one end connected to the exhaust pipe through which the exhaust gas flows. An EGR gas pipe 30 is connected to the branch portion 24 of the intake pipe 20.

図１に示すように、集合ＥＧＲガス管３１ｃの途中には、ＥＧＲガスの吸気管２０への流入と遮断を制御するためのＥＧＲバルブ３２が設けられている。また、ＥＧＲガス管３０におけるＥＧＲバルブ３２の上流には、排気管より導入されるＥＧＲガスを冷却するためのＥＧＲクーラ３３ａ，３３ｂが設けられている。ＥＧＲガス管３０は円管である。   As shown in FIG. 1, an EGR valve 32 for controlling the flow of the EGR gas into the intake pipe 20 and the shutoff thereof is provided in the middle of the collective EGR gas pipe 31c. Further, upstream of the EGR valve 32 in the EGR gas pipe 30 are provided EGR coolers 33a and 33b for cooling the EGR gas introduced from the exhaust pipe. The EGR gas pipe 30 is a circular pipe.

図２に示すように、ＥＧＲガス管３０は、分岐部２４において、Ｙ軸に沿って延びている。ＥＧＲガス管３０を介して吸気管２０にＥＧＲガスが導入され、導入されたＥＧＲガスは左右のバンク５１，５２の吸気時に、それぞれ、新気吸気管２１より左右のバンク５１，５２へ流入する新気に合流する。また、新気吸気管２１における分岐部２４よりも吸気上流側にはディーゼルスロットル（弁）２７が設けられている。ディーゼルスロットル２７の開閉制御により、軽負荷時などにおいて、ＥＧＲガス管３０から吸気管２０への多量のＥＧＲガスの導入を可能としている。   As shown in FIG. 2, the EGR gas pipe 30 extends along the Y axis at the branch portion 24. EGR gas is introduced into the intake pipe 20 via the EGR gas pipe 30, and the introduced EGR gas flows into the left and right banks 51, 52 from the fresh air intake pipe 21 when the left and right banks 51, 52 are inhaled, respectively. Meet new. A diesel throttle (valve) 27 is provided on the intake air upstream side of the branch portion 24 in the fresh air intake pipe 21. By opening / closing control of the diesel throttle 27, a large amount of EGR gas can be introduced from the EGR gas pipe 30 to the intake pipe 20 at a light load or the like.

ＥＧＲガス管３０の吸気管２０への連結位置は、ディーゼルスロットル２７よりも下流側となっている。これは、ＥＧＲガス管３０から吸気管２０に導入されるＥＧＲガスに含まれるススや未燃燃料などの成分がディーゼルスロットル２７に付着して動作不良となるのを防止するためである。分岐部２４はディーゼルスロットル２７から離間した位置に形成されているため、ここにＥＧＲガス管３０が連結される。また、ＥＧＲガス管３０は吸気管２０に対し分岐部２４において一点で連結させることにより、構造を複雑化させることなくＥＧＲガスを新気に合流させることを可能としている。つまり、ＥＧＲガス管を分岐部２４よりも下流で吸気管２０に連結しようとすると、ＥＧＲガス管の吸気管２０への接続部を分岐管２２，２３に対応させて分岐させる必要があり、結果としてＥＧＲガス管の構造が複雑になってしまう。このようなＥＧＲガス管の構造の複雑化を回避すべく、本実施形態ではＥＧＲガス管３０を分岐部２４において一点で連結している。   The connection position of the EGR gas pipe 30 to the intake pipe 20 is on the downstream side of the diesel throttle 27. This is to prevent components such as soot and unburned fuel contained in the EGR gas introduced from the EGR gas pipe 30 into the intake pipe 20 from adhering to the diesel throttle 27 and causing malfunction. Since the branch portion 24 is formed at a position separated from the diesel throttle 27, the EGR gas pipe 30 is connected thereto. Further, the EGR gas pipe 30 is connected to the intake pipe 20 at a single point at the branch portion 24, thereby allowing the EGR gas to merge with fresh air without complicating the structure. That is, if the EGR gas pipe is to be connected to the intake pipe 20 downstream of the branch portion 24, the connection portion of the EGR gas pipe to the intake pipe 20 needs to be branched corresponding to the branch pipes 22 and 23. As a result, the structure of the EGR gas pipe becomes complicated. In order to avoid such a complicated structure of the EGR gas pipe, in this embodiment, the EGR gas pipe 30 is connected to the branch portion 24 at one point.

図２、図３、図４（ａ）、図４（ｂ）に示すように、吸気管２０内に隔壁部材４０が配置されている。隔壁部材４０は、図４（ａ）に示すように、分岐部２４において新気吸気管２１に対向配置された頂上部４３と、頂上部４３より分岐管２２，２３に沿って両側に延びる斜状板部４１、斜状板部４２を有している。具体的には、図４（ａ）に示すように、斜状板部４１は新気吸気管２１の中央部に対向する頂上部４３を基点として分岐管２２が延びる方向に下がり傾斜で延在する壁として形成されており、斜状板部４２は頂上部４３から分岐管２３が延びる方向に下がり傾斜で延在する壁として形成されている。なお、図４（ａ）において、斜状板部４１がＸ軸となす傾斜角度と斜状板部４２がＸ軸となす傾斜角度は等しくなっている。また、図４（ａ）に示すように、隔壁部材４０の頂上部（斜状板部４１と斜状板部４２の連結部）４３は新気吸気管２１側に凸の円弧状に形成されている。板状の隔壁部材４０はＥＧＲガス管３０から吸気管２０に導入されるＥＧＲガスの新気上流側への逆流を防止するとともに、新気吸気管２１より導入される新気の整流板として機能する。つまり、新気吸気管２１より新気が導入されると、右バンク５１で吸気される場合には、隔壁部材４０の斜状板部４１に沿って右バンク５１に向かう流れＣ１０が形成され、同様に左バンク５２で吸気される場合には、斜状板部４２に沿って左バンク５２に向かう流れＣ１１が形成される。このように、隔壁部材４０は、新気吸気管２１の開口部２１ａに向かって凸となる形状を有し、新気吸気管２１から導入される新気を左右のバンクへスムーズに導く整流板として機能する。   As shown in FIGS. 2, 3, 4 (a), and 4 (b), a partition member 40 is disposed in the intake pipe 20. As shown in FIG. 4A, the partition member 40 includes a top portion 43 disposed opposite to the fresh air intake pipe 21 at the branch portion 24, and a slant extending from the top portion 43 to both sides along the branch tubes 22 and 23. The plate portion 41 and the oblique plate portion 42 are provided. Specifically, as shown in FIG. 4A, the slanted plate portion 41 extends with a downward slope in the direction in which the branch pipe 22 extends, with the top 43 facing the center of the fresh air intake pipe 21 as a base point. The slanted plate portion 42 is formed as a wall extending downwardly from the top portion 43 in the direction in which the branch pipe 23 extends. In FIG. 4A, the inclination angle formed by the oblique plate portion 41 and the X axis is equal to the inclination angle formed by the oblique plate portion 42 and the X axis. Further, as shown in FIG. 4A, the top portion (the connecting portion between the inclined plate portion 41 and the inclined plate portion 42) 43 of the partition wall member 40 is formed in a convex arc shape on the fresh air intake pipe 21 side. ing. The plate-like partition member 40 prevents the backflow of EGR gas introduced from the EGR gas pipe 30 into the intake pipe 20 to the upstream side of fresh air, and functions as a rectifying plate for fresh air introduced from the fresh air intake pipe 21. To do. That is, when fresh air is introduced from the fresh air intake pipe 21, when the air is taken in by the right bank 51, a flow C <b> 10 toward the right bank 51 is formed along the slanted plate portion 41 of the partition member 40, Similarly, when air is taken in by the left bank 52, a flow C <b> 11 toward the left bank 52 is formed along the inclined plate portion 42. In this way, the partition member 40 has a shape that is convex toward the opening 21a of the fresh air intake pipe 21, and a rectifying plate that smoothly guides fresh air introduced from the fresh air intake pipe 21 to the left and right banks. Function as.

吸気管２０における隔壁部材４０の頂上部４３の新気吸気管２１と対向する側と反対側には、Ｙ方向に向かって延びるＥＧＲガス管３０が接続されて吸気管２０に開口している。このため、図４（ａ）に示すように、吸気管２０の分岐部２４において、隔壁部材４０の新気吸気管２１と対向する側と反対側に形成される断面略三角形状の空間（隔壁部材４０と吸気管２０の内面とで囲まれた空間）が、ＥＧＲガスが滞留するＥＧＲガス溜め室Ｒ１として機能する。即ち、隔壁部材４０により、吸気管２０内にＥＧＲガスを滞留させるためのＥＧＲガス溜め室Ｒ１が区画形成される。ＥＧＲガス管３０よりＥＧＲガス溜め室Ｒ１に流入してＥＧＲガス溜め室Ｒ１に滞留するＥＧＲガスは第１バンク用流路としての右バンク用流路Ｃ１または第２バンク用流路としての左バンク用流路Ｃ２を介して左右のバンク５１，５２に流出する。具体的には、新気吸気管２１より導入される新気及びＥＧＲガス管３０より導入されてＥＧＲガス溜め室Ｒ１に溜められたＥＧＲガスは、右バンク５１と左バンク５２の吸気に応じて、それぞれ、分岐管２２または分岐管２３に流れる。   An EGR gas pipe 30 extending in the Y direction is connected to and opened to the intake pipe 20 on the opposite side of the top 43 of the partition wall member 40 in the intake pipe 20 from the side facing the fresh air intake pipe 21. For this reason, as shown in FIG. 4A, in the branching portion 24 of the intake pipe 20, a space (partition wall) having a substantially triangular cross section formed on the opposite side of the partition member 40 from the side facing the fresh air intake pipe 21. A space surrounded by the member 40 and the inner surface of the intake pipe 20) functions as an EGR gas reservoir chamber R1 in which EGR gas stays. That is, the partition member 40 defines an EGR gas reservoir chamber R1 for retaining EGR gas in the intake pipe 20. The EGR gas flowing into the EGR gas reservoir chamber R1 from the EGR gas pipe 30 and staying in the EGR gas reservoir chamber R1 is the right bank channel C1 as the first bank channel or the left bank as the second bank channel. It flows out to the left and right banks 51 and 52 through the flow path C2. Specifically, the fresh air introduced from the fresh air intake pipe 21 and the EGR gas introduced from the EGR gas pipe 30 and accumulated in the EGR gas reservoir chamber R1 correspond to the intake of the right bank 51 and the left bank 52. , Flow into the branch pipe 22 or the branch pipe 23, respectively.

このようにして、ＥＧＲガス管３０が吸気管２０の分岐部２４に接続され、吸気管２０内におけるＥＧＲガス管３０の開口部３０ａの周囲に、ＥＧＲガスが流入するとともにＥＧＲガスが右バンク５１及び左バンク５２に向けて流出するＥＧＲガス溜め室Ｒ１を区画形成するための隔壁部材４０が配置されている。   In this way, the EGR gas pipe 30 is connected to the branch portion 24 of the intake pipe 20, and EGR gas flows into the periphery of the opening 30 a of the EGR gas pipe 30 in the intake pipe 20 and the EGR gas flows to the right bank 51. In addition, a partition member 40 is provided for partitioning the EGR gas reservoir chamber R1 flowing out toward the left bank 52.

ＥＧＲガス溜め室Ｒ１におけるＥＧＲガスが右バンク５１に向けて流出する右バンク用流路Ｃ１での有効断面積及び左バンク５２に向けて流出する左バンク用流路Ｃ２での有効断面積が、ＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さくされている。   The effective sectional area in the right bank channel C1 from which the EGR gas in the EGR gas reservoir chamber R1 flows out toward the right bank 51 and the effective sectional area in the left bank channel C2 from which it flows out toward the left bank 52 are: The flow path cross-sectional area S3 at the opening 30a of the EGR gas pipe 30 is made smaller.

詳しくは、図４（ａ），（ｂ）に示すように、右バンク用流路Ｃ１での実断面積Ｓ１及び左バンク用流路Ｃ２での実断面積Ｓ２が、ＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さい。これにより、右バンク用流路Ｃ１での有効断面積及び左バンク用流路Ｃ２での有効断面積がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さくされている。   Specifically, as shown in FIGS. 4A and 4B, the actual sectional area S1 in the right bank channel C1 and the actual sectional area S2 in the left bank channel C2 are the opening of the EGR gas pipe 30. It is smaller than the channel cross-sectional area S3 at the portion 30a. Thereby, the effective sectional area in the right bank channel C1 and the effective sectional area in the left bank channel C2 are made smaller than the channel sectional area S3 in the opening 30a of the EGR gas pipe 30.

次に、作用について説明する。
新気吸気管２１から新気が導入される。分岐部２４においてＥＧＲガス管３０から導入されてＥＧＲガス溜め室Ｒ１に溜められたＥＧＲガスが新気に合流する。分岐部２４において新気とＥＧＲガスが合流した後の混合気が分岐管２２，２３を通して左右のバンク５１，５２に供給される。 Next, the operation will be described.
Fresh air is introduced from the fresh air intake pipe 21. The EGR gas introduced from the EGR gas pipe 30 in the branch portion 24 and stored in the EGR gas storage chamber R1 joins fresh air. The air-fuel mixture after the fresh air and EGR gas merge at the branching section 24 is supplied to the left and right banks 51 and 52 through the branch pipes 22 and 23.

分岐部２４において吸気管２０に配置された隔壁部材４０によりＥＧＲガス溜め室Ｒ１が区画形成され、右バンク用流路Ｃ１での実断面積Ｓ１及び左バンク用流路Ｃ２での実断面積Ｓ２がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さく形成されている。つまり、流入側の面積よりも流出側の面積が小さく形成されている。これにより、ＥＧＲガス溜め室Ｒ１に所定量のＥＧＲガスを滞留させておくことが可能となっている。左バンク吸気時には、ＥＧＲガス溜め室Ｒ１に溜められたＥＧＲガスのうち左バンク用流路Ｃ２より流出する一定量のＥＧＲガスが新気吸気管２１より導入される新気とともに左バンク５２に流入し、右バンク吸気時には、ＥＧＲガス溜め室Ｒ１に溜められたＥＧＲガスのうち右バンク用流路Ｃ１より流出する一定量のＥＧＲガスが新気吸気管２１を介して導入される新気とともに右バンク５１に流入するので、結果としてＥＧＲガスは左右のバンクの各気筒に均等に分配されることとなる。   An EGR gas reservoir chamber R1 is defined by the partition member 40 disposed in the intake pipe 20 at the branch portion 24, and an actual sectional area S1 in the right bank channel C1 and an actual sectional area S2 in the left bank channel C2. Is smaller than the flow path cross-sectional area S3 at the opening 30a of the EGR gas pipe 30. That is, the area on the outflow side is smaller than the area on the inflow side. As a result, a predetermined amount of EGR gas can be retained in the EGR gas reservoir chamber R1. During left bank intake, a certain amount of EGR gas outflowing from the left bank channel C2 out of the EGR gas stored in the EGR gas reservoir chamber R1 flows into the left bank 52 together with fresh air introduced from the fresh air intake pipe 21. During intake of the right bank, a certain amount of EGR gas flowing out of the right bank channel C1 out of the EGR gas stored in the EGR gas reservoir chamber R1 is moved to the right together with fresh air introduced through the fresh air intake pipe 21. Since it flows into the bank 51, as a result, the EGR gas is evenly distributed to the cylinders of the left and right banks.

このようにして、左右のバンクへのＥＧＲ率（新気とＥＧＲガスの割合）を均等化して６気筒のＥＧＲ率を揃えることができる。つまり、各種の運転条件（負荷条件下）においても左右のバンクのＥＧＲ率の差を小さくでき、ＥＧＲ分配改善が図られる。また、板状の隔壁部材４０を配置したことによりディーゼルスロットル２７へのＥＧＲガスの吹き返しの低減が図られる。即ち、ＥＧＲガスについて新気の上流側への吹き返しが発生するとディーゼルスロットル２７にＥＧＲガスが達することによりディーゼルスロットル２７にススや未燃燃料などの不純物成分が付着してしまう虞があるが、これを抑制することができる（ディーゼルスロットル２７の動作不良を回避できる）。   In this way, it is possible to equalize the EGR rates of the six cylinders by equalizing the EGR rate (the ratio of fresh air and EGR gas) to the left and right banks. That is, even under various operating conditions (under load conditions), the difference between the EGR rates of the left and right banks can be reduced, and the EGR distribution can be improved. Further, by arranging the plate-like partition member 40, the blow-back of the EGR gas to the diesel throttle 27 can be reduced. That is, when the EGR gas blows back to the upstream side, the EGR gas reaches the diesel throttle 27, and there is a possibility that impurities components such as soot and unburned fuel adhere to the diesel throttle 27. (A malfunction of the diesel throttle 27 can be avoided).

また、隔壁部材４０を上に凸の板形状とすることにより、新気を左右のバンクへスムーズに導くための整流板として機能させている。具体的には、図４（ａ）に示すように、隔壁部材４０が、新気吸気管２１より導入される新気を右バンク５１に対しては流路Ｃ１０に沿った流れとして流すとともに左バンク５２に対しては流路Ｃ１１に沿った流れとして流す。その結果、新気の左右のバンクへの流れが円滑な流れとなり、新気吸入時の圧損低減が図られる。   Further, by forming the partition wall member 40 as a convex plate shape, the partition member 40 functions as a rectifying plate for smoothly guiding fresh air to the left and right banks. Specifically, as shown in FIG. 4A, the partition member 40 causes the fresh air introduced from the fresh air intake pipe 21 to flow to the right bank 51 as a flow along the flow path C10 and to the left. The bank 52 flows as a flow along the flow path C11. As a result, the flow of fresh air to the left and right banks is smooth, and the pressure loss during the intake of fresh air is reduced.

また、一点でＥＧＲガス管３０を吸気管２０に連結することによりＥＧＲガスを新気に合流させているので、ＥＧＲガス管を分岐させて吸気管の左右のバンクに対応する分岐管にそれぞれ連結しているものに比べてコスト低減が図られる。   In addition, since the EGR gas pipe 30 is connected to the intake pipe 20 at one point so that the EGR gas is merged with fresh air, the EGR gas pipe is branched and connected to the branch pipes corresponding to the left and right banks of the intake pipe. The cost can be reduced compared to what is being done.

本実施形態では、ＥＧＲガス管３０の連結部における吸気管２０内に配置された隔壁部材４０によりＥＧＲガス溜め室Ｒ１が区画形成され、ＥＧＲガスが流入するとともにＥＧＲガスが左右のバンク５１，５２に向けて流出する。これにより、ＥＧＲガス管３０を分岐してＥＧＲガスを左右のバンクに分配するのではなく、吸気管２０にＥＧＲガス管３０を一点で連結することによりＥＧＲガスを合流させ、吸気管２０内でＥＧＲガスを分配することにより形状の複雑化を抑えることができる。   In the present embodiment, the EGR gas reservoir chamber R1 is defined by the partition member 40 disposed in the intake pipe 20 at the connecting portion of the EGR gas pipe 30, and the EGR gas flows in and the EGR gas flows into the left and right banks 51, 52. Spills towards As a result, the EGR gas pipe 30 is connected to the intake pipe 20 at a single point instead of branching the EGR gas pipe 30 and distributing the EGR gas to the left and right banks. Distributing the EGR gas can suppress the complexity of the shape.

また、ＥＧＲガス溜め室Ｒ１におけるＥＧＲガスが右バンク５１に向けて流出する右バンク用流路Ｃ１での有効断面積及び左バンク５２に向けて流出する左バンク用流路Ｃ２での有効断面積がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さくされている。これにより、新気及びＥＧＲガスは右バンク５１と左バンク５２とで交互に吸気されるが、この脈動に対して左右圧損を同じにするだけでなくＥＧＲガスで満たされた容積を確保しているので、左右のバンク５１，５２に流すＥＧＲガスの量を均等化することができる。   Further, the effective sectional area in the right bank channel C1 from which the EGR gas in the EGR gas reservoir chamber R1 flows out toward the right bank 51 and the effective sectional area in the left bank channel C2 from which it flows out toward the left bank 52 are displayed. Is smaller than the flow path cross-sectional area S3 at the opening 30a of the EGR gas pipe 30. As a result, fresh air and EGR gas are alternately sucked in the right bank 51 and the left bank 52, but not only the right and left pressure loss is made equal to this pulsation, but also a volume filled with EGR gas is secured. Therefore, the amount of EGR gas flowing to the left and right banks 51 and 52 can be equalized.

その結果、形状の複雑化を回避しつつ左右のバンクに流すＥＧＲガスの量を均等化することができる。
上記実施形態によれば、以下のような効果を得ることができる。 As a result, it is possible to equalize the amount of EGR gas flowing to the left and right banks while avoiding complicated shapes.
According to the above embodiment, the following effects can be obtained.

（１）内燃機関の吸気装置１０の構成として、ＥＧＲガス管３０が吸気管２０の分岐部２４に接続されている。吸気管２０内におけるＥＧＲガス管３０の開口部３０ａの周囲に、ＥＧＲガスが流入するとともにＥＧＲガスが右バンク５１及び左バンク５２に向けて流出するＥＧＲガス溜め室Ｒ１を区画形成するための隔壁部材４０が配置されている。ＥＧＲガス溜め室Ｒ１におけるＥＧＲガスが右バンク５１に向けて流出する右バンク用流路Ｃ１での有効断面積及び左バンク５２に向けて流出する左バンク用流路Ｃ２での有効断面積がＥＧＲガス管３０の開口部３０ａでの流路断面積より小さくされている。よって、右バンク及び左バンクに流すＥＧＲガスの量を均等化することができる。   (1) As a configuration of the intake device 10 for the internal combustion engine, an EGR gas pipe 30 is connected to a branch portion 24 of the intake pipe 20. A partition for defining an EGR gas reservoir chamber R1 into which EGR gas flows and the EGR gas flows out toward the right bank 51 and the left bank 52 around the opening 30a of the EGR gas pipe 30 in the intake pipe 20. A member 40 is arranged. The effective cross-sectional area in the right bank channel C1 through which the EGR gas in the EGR gas reservoir chamber R1 flows out toward the right bank 51 and the effective cross-sectional area in the left bank channel C2 through which it flows out toward the left bank 52 are EGR. The flow path cross-sectional area at the opening 30 a of the gas pipe 30 is made smaller. Therefore, the amount of EGR gas flowing to the right bank and the left bank can be equalized.

（２）右バンク用流路Ｃ１での実断面積Ｓ１及び左バンク用流路Ｃ２での実断面積Ｓ２がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さいことにより、右バンク用流路Ｃ１での有効断面積及び左バンク用流路Ｃ２での有効断面積がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ３より小さくされている。よって、実用的である。   (2) Since the actual sectional area S1 in the right bank channel C1 and the actual sectional area S2 in the left bank channel C2 are smaller than the channel sectional area S3 in the opening 30a of the EGR gas pipe 30, The effective sectional area in the bank channel C1 and the effective sectional area in the left bank channel C2 are smaller than the channel sectional area S3 in the opening 30a of the EGR gas pipe 30. Therefore, it is practical.

（３）隔壁部材４０は、新気吸気管２１の開口部２１ａに向かって凸となる形状を有するので、新気の流路での流れを滑らかにでき、新気流の抵抗を小さくすることができる。
実施形態は前記に限定されるものではなく、例えば、次のように具体化してもよい。 (3) Since the partition wall member 40 has a convex shape toward the opening 21a of the fresh air intake pipe 21, the flow in the fresh air flow path can be smoothed, and the resistance of the fresh air current can be reduced. it can.
The embodiment is not limited to the above, and may be embodied as follows, for example.

・図４（ａ）に代わる図５に示すように、板材よりなる隔壁部材６０はＸ方向に真っ直ぐに延びていてもよい。図５の場合、吸気管２０には、外側に凸となる円弧部６１が形成され、隔壁部材６０と円弧部６１との間においてＥＧＲガス管３０が開口している。   As shown in FIG. 5 instead of FIG. 4A, the partition member 60 made of a plate material may extend straight in the X direction. In the case of FIG. 5, the intake pipe 20 is formed with an arc portion 61 that protrudes outward, and the EGR gas pipe 30 opens between the partition wall member 60 and the arc portion 61.

・図４（ａ）に代わる図６に示すように、ＥＧＲガス管３０は、分岐部２４において、Ｚ方向に延びており、ＥＧＲガスの導入方向はＺ方向からでもよい。
・図４（ａ）に代わる図７に示すように、分岐部２４の形状として、新気吸気管２１と分岐管２２，２３とは逆Ｙの字状であってもよく、この形状に合わせて隔壁部材７０を設けてもよい。要は、分岐後の配管形状に合わせて隔壁部材７０を設ければよい。 As shown in FIG. 6 instead of FIG. 4A, the EGR gas pipe 30 extends in the Z direction at the branching portion 24, and the EGR gas introduction direction may be from the Z direction.
As shown in FIG. 7 instead of FIG. 4 (a), the shape of the branch portion 24 may be a reverse Y-shape of the fresh air intake pipe 21 and the branch pipes 22, 23. A partition member 70 may be provided. In short, the partition member 70 may be provided in accordance with the pipe shape after branching.

・図４（ａ）に代わる図８に示すように、隔壁部材４０における斜状板部４１の先端側に折曲部８０を設けるとともに斜状板部４２の先端側に折曲部８１を設けてもよい。この場合には斜状板部４１と折曲部８０との境界及び斜状板部４２と折曲部８１との境界部が最小流路部となる。   As shown in FIG. 8 instead of FIG. 4A, a bent portion 80 is provided on the front end side of the slanted plate portion 41 in the partition wall member 40 and a bent portion 81 is provided on the front end side of the slanted plate portion 42. May be. In this case, the boundary between the inclined plate portion 41 and the bent portion 80 and the boundary portion between the inclined plate portion 42 and the bent portion 81 are the minimum flow path portions.

・図４（ａ），（ｂ）に代わり図９（ａ），（ｂ）に示すようにしてもよい。有効断面積は流路の実際の断面積に流量係数をかけたもの、即ち、有効断面積＝（流量係数）×（実流路断面積）であるので、以下の構成としてもよい。   -Instead of FIG. 4 (a), (b), you may make it show in FIG. 9 (a), (b). Since the effective cross-sectional area is obtained by multiplying the actual cross-sectional area of the flow path by the flow coefficient, that is, effective cross-sectional area = (flow coefficient) × (actual flow cross-sectional area), the following configuration may be adopted.

右バンク用流路Ｃ１での実断面積Ｓ１１及び左バンク用流路Ｃ２での実断面積Ｓ１２がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ１３より大きい。また、ＥＧＲガス溜め室Ｒ１におけるＥＧＲガスの流路Ｃ１，Ｃ２に、流量係数を小さくするために急激に断面積が小さくなる絞りとしての垂直板部９２，９３が形成されている。つまり、隔壁部材９０は、Ｘ方向に延びる平板部９１と、平板部９１の先端からＺ方向に延びる絞りとして垂直板部９２，９３と、垂直板部（絞り）９２，９３の先端からＸ方向に延びる平板部９４，９５を有する。これにより、垂直板部（絞り）９２，９３により、右バンク用流路Ｃ１での有効断面積及び左バンク用流路Ｃ２での有効断面積がＥＧＲガス管３０の開口部３０ａでの流路断面積Ｓ１３より小さくされている。   The actual sectional area S11 in the right bank channel C1 and the actual sectional area S12 in the left bank channel C2 are larger than the channel sectional area S13 in the opening 30a of the EGR gas pipe 30. In addition, vertical plates 92 and 93 are formed in the EGR gas passages C1 and C2 in the EGR gas reservoir chamber R1 as throttles whose sectional area is abruptly reduced in order to reduce the flow coefficient. That is, the partition wall member 90 includes a flat plate portion 91 extending in the X direction, vertical plate portions 92 and 93 as stops extending in the Z direction from the front end of the flat plate portion 91, and X direction from the front ends of the vertical plate portions (stops) 92 and 93. Flat plate portions 94 and 95 extending in the horizontal direction. As a result, the vertical plate portions (throttles) 92 and 93 cause the effective cross-sectional area in the right bank flow path C1 and the effective cross-sectional area in the left bank flow path C2 to flow in the opening 30a of the EGR gas pipe 30. It is smaller than the cross-sectional area S13.

・内燃機関はＶ型エンジンに限らず、ボクサーエンジン、Ｗ型エンジンなど第１バンクと第２バンクに分岐しているエンジンに適用可能である。
・図４（ａ）において隔壁部材４０を含めた分岐部２４の形状として左右対称でなくてもＥＧＲガスの分配性に有用である。 The internal combustion engine is not limited to a V-type engine, but can be applied to an engine that branches into a first bank and a second bank, such as a boxer engine and a W-type engine.
In FIG. 4A, the shape of the branching portion 24 including the partition wall member 40 is useful for the distribution of EGR gas even if it is not bilaterally symmetric.

・隔壁部材４０は板材で構成しなくてもよい。
・ＥＧＲガス管は新気吸気管に対し直交するように連結されているが、斜め方向から連結してもよい。 -The partition member 40 does not need to be comprised with a board | plate material.
-Although the EGR gas pipe is connected so as to be orthogonal to the fresh air intake pipe, it may be connected from an oblique direction.

・内燃機関はディーゼルエンジン以外でもよく、例えばガソリンエンジンでもよい。また、内燃機関の気筒数は問わない。   The internal combustion engine may be other than a diesel engine, for example, a gasoline engine. Further, the number of cylinders of the internal combustion engine does not matter.

１０…内燃機関の吸気装置、２０…吸気管、２１…新気吸気管、２１ａ…開口部、２２…分岐管、２３…分岐管、２４…分岐部、３０…ＥＧＲガス管、３０ａ…開口部、４０…隔壁部材、５１…右バンク、５２…左バンク、９０…隔壁部材、９２…垂直板部、９３…垂直板部、Ｃ１…右バンク用流路、Ｃ２…左バンク用流路、Ｒ１…ＥＧＲガス溜め室。   DESCRIPTION OF SYMBOLS 10 ... Intake device of internal combustion engine, 20 ... Intake pipe, 21 ... Fresh air intake pipe, 21a ... Opening part, 22 ... Branch pipe, 23 ... Branch pipe, 24 ... Branch part, 30 ... EGR gas pipe, 30a ... Opening part 40 ... partition member, 51 ... right bank, 52 ... left bank, 90 ... partition member, 92 ... vertical plate part, 93 ... vertical plate part, C1 ... right bank channel, C2 ... left bank channel, R1 ... EGR gas reservoir.

Claims (4)

新気が流れる１本の新気吸気管に分岐部を介して第１バンク用と第２バンク用の２本の分岐管が接続された吸気管と、
前記吸気管にＥＧＲガスを導入するためのＥＧＲガス管と、
を備える内燃機関の吸気装置であって、
前記ＥＧＲガス管が前記吸気管の前記分岐部に接続され、
前記吸気管内における前記ＥＧＲガス管の開口部の周囲に、前記ＥＧＲガス管から前記吸気管に導入されるＥＧＲガスの新気上流側への逆流を防止するとともに、前記新気吸気管より導入される新気を第１バンク及び第２バンクへと導く隔壁部材が配置され、
前記隔壁部材は、前記隔壁部材と対向する前記吸気管の内面との間に、前記ＥＧＲガス管から導入されるＥＧＲガスを前記吸気管内に滞留させるＥＧＲガス溜め室を区画形成するとともに、前記ＥＧＲガス溜め室に滞留したＥＧＲガスを第１バンクと第２バンクの吸気に応じて流出させる第１バンク用流路及び第２バンク用流路を区画形成しており、
前記第１バンク用流路での有効断面積及び前記第２バンク用流路での有効断面積が前記ＥＧＲガス管の開口部での流路断面積より小さくされており、
前記第１バンク用流路及び前記第２バンク用流路は、前記ＥＧＲガス管の開口部側から前記第１バンク用の分岐管又は前記第２バンク用の分岐管に向けて流路が縮小していることを特徴とする内燃機関の吸気装置。 An intake pipe in which two branch pipes for the first bank and the second bank are connected to one fresh air intake pipe through which a fresh air flows through a branch portion;
An EGR gas pipe for introducing EGR gas into the intake pipe;
An intake device for an internal combustion engine comprising:
The EGR gas pipe is connected to the branch of the intake pipe;
Around the opening of the EGR gas pipe in the intake pipe, thereby preventing backflow from the EGR gas pipe to the fresh air upstream of the EGR gas introduced into the intake pipe, it is introduced from the fresh air intake pipe A partition member for guiding fresh air to the first bank and the second bank is disposed,
The partition member defines an EGR gas reservoir chamber in which EGR gas introduced from the EGR gas pipe is retained in the intake pipe between the inner surface of the intake pipe facing the partition member, and the EGR A first bank flow path and a second bank flow path for allowing the EGR gas retained in the gas reservoir chamber to flow out in accordance with the intake air of the first bank and the second bank;
The effective area of the effective cross-sectional area and flow path for the second bank in the first bank passage are smaller than the flow path cross-sectional area at the opening of the EGR gas pipe,
The channel for the first bank and the channel for the second bank are reduced from the opening side of the EGR gas pipe toward the branch pipe for the first bank or the branch pipe for the second bank. an intake system for an internal combustion engine, characterized in that it is. 前記第１バンク用流路での実断面積及び前記第２バンク用流路での実断面積が前記ＥＧＲガス管の開口部での流路断面積より小さいことにより、前記第１バンク用流路での有効断面積及び第２バンク用流路での有効断面積が前記ＥＧＲガス管の開口部での流路断面積より小さくされていることを特徴とする請求項１に記載の内燃機関の吸気装置。   Since the actual sectional area in the first bank channel and the actual sectional area in the second bank channel are smaller than the channel sectional area in the opening of the EGR gas pipe, the first bank channel 2. The internal combustion engine according to claim 1, wherein an effective cross-sectional area at the road and an effective cross-sectional area at the second bank flow path are smaller than a flow path cross-sectional area at the opening of the EGR gas pipe. Inhalation device. 前記第１バンク用流路での実断面積及び前記第２バンク用流路での実断面積が前記ＥＧＲガス管の開口部での流路断面積より大きく、かつ、前記ＥＧＲガス溜め室におけるＥＧＲガスの流路での絞りにより、前記第１バンク用流路での有効断面積及び第２バンク用流路での有効断面積が前記ＥＧＲガス管の開口部での流路断面積より小さくされていることを特徴とする請求項１に記載の内燃機関の吸気装置。   The actual sectional area in the first bank channel and the actual sectional area in the second bank channel are larger than the channel sectional area in the opening of the EGR gas pipe, and in the EGR gas reservoir chamber. Due to the restriction in the EGR gas channel, the effective sectional area in the first bank channel and the effective sectional area in the second bank channel are smaller than the channel sectional area in the opening of the EGR gas pipe. The intake device for an internal combustion engine according to claim 1, wherein the intake device is provided. 前記隔壁部材は、新気吸気管の開口部に向かって凸となる形状を有することを特徴とする請求項１〜３のいずれか１項に記載の内燃機関の吸気装置。   The intake device for an internal combustion engine according to any one of claims 1 to 3, wherein the partition member has a shape that protrudes toward an opening of a fresh air intake pipe.
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